JP5348924B2 - Screw fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an inexpensive and space-saving screw compressor having a shaft seal structure on the discharge side of a rotor shaft. <P>SOLUTION: This screw fluid machine 1 is provided for compressing object gas or converting expansion force of the object gas into torque by a female-male meshing screw rotor 4 stored in a rotor chamber 3 formed in a housing 2, and is formed by arranging a noncontact seal 15 and a first lip seal 16 in order from the screw rotor 4 side between the screw rotor 4 and a high pressure side bearing 11 of the rotor shaft 7, and is provided with a first communicating hole 22 for communicating a first seal space 18 between the noncontact seal 15 and the first lip seal 16 with a space of useful pressure or less of the first lip seal 16 and a lubricating fluid supply flow passage 24 for supplying a lubricating fluid to the first seal space 18. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

  The present invention relates to a screw fluid machine.

  Screw fluid machines, such as a screw compressor that compresses the target gas with a screw rotor that engages the male and female in the rotor chamber, and a screw expander that converts the expansion of the target gas into rotational energy, seal the target gas in the system. Alternatively, a shaft seal structure is provided between the screw rotor of the rotor shaft and the bearing in order to prevent outside air from being mixed into the target gas.

  As described in Patent Document 1, in the conventional screw compressor, a lip seal is used as a suction side shaft seal device, and a mechanical seal is used as a discharge side shaft seal device.

  The lip seal is an inexpensive and space-saving shaft seal device, but generally the maximum pressure that can be sealed is about 0.03 MPa. For this reason, the lip seal can be used only for the shaft seal on the suction side of the low pressure because the shaft seal may be insufficient on the discharge side where the pressure is high or the durability may be significantly reduced. On the other hand, the mechanical seal is capable of high-pressure shaft sealing, but has a problem that it is very expensive and requires a large space for installation.

  In Patent Document 2, a non-contact seal such as a labyrinth seal is provided on the screw rotor side between the screw rotor and the bearing, a lip seal is provided on the bearing side, and a space between the non-contact seal and the lip seal is provided. An invention is described in which excessive pressure is not applied to the lip seal by communicating with a low pressure space.

However, even in the invention of Patent Document 2, when the temperature of the target gas is high, the temperature of the lip seal rises due to the slightly leaked high temperature target gas. Lip seals generally have a large coefficient of thermal expansion, and even if the pressure in the seal space does not rise, there is a problem that the contact pressure against the rotor shaft increases due to temperature rise and is easily damaged.
JP 2000-45948 A JP 2007-132243 A

  In view of the above problems, an object of the present invention is to provide a screw compressor having a shaft seal structure that is inexpensive, space-saving, and has a reliable seal on the high-pressure side of a rotor shaft.

In order to solve the above-mentioned problems, according to the present invention, a screw that compresses a target gas by a male and female screw rotor housed in a rotor chamber formed in a housing or converts an expansion force of the target gas into a rotational force. in the fluid machine, between the high pressure side of the bearing of the rotor shaft of the screw rotors and the screw rotor, in order from the screw rotor side, move the lubricating fluid into the rotor chamber side by a rotation force of the rotor shaft A non-contact seal having a spiral groove or a protrusion and a first lip seal are disposed, and a first seal space between the non-contact seal and the first lip seal is less than a working pressure of the first lip seal. A first communication hole communicating with the space, and a lubricating flow for supplying the lubricating fluid to the first seal space by supplying a lubricating fluid in the middle of the spiral groove or projection And that provided a supply channel.

  According to this configuration, while preventing excessive pressure from being applied to the first lip seal by the first communication hole, and further cooling the lip seal with the lubricating fluid supplied to the first seal space, Friction between the rotor shaft and the first lip seal can be extended.

According to this configuration, the target gas can be sealed by the pressure that moves the lubricating fluid to the rotor chamber side by filling the gap of the non-contact seal with the lubricating fluid and the spiral groove or protrusion.

  Further, in the screw fluid machine of the present invention, a second lip seal is disposed between the first lip seal and the bearing, and a second seal between the first lip seal and the second lip seal. You may provide the 2nd communicating hole which connects space to the low pressure space of substantially atmospheric pressure.

  According to this configuration, even if the pressure in the first seal space is higher than atmospheric pressure, the second lip seal can seal the target gas, the lubricating fluid, and the like so as not to flow into the bearing side.

  In the screw fluid machine of the present invention, the target gas may be steam, and the lubricating fluid may be condensed water of the target gas.

  According to this configuration, the lubricating fluid can be supplied to the screw fluid machine by the pressure of the condensed water, and an incidental facility such as a pump is not necessary.

  As described above, according to the present invention, the first communication hole is provided in the first seal space immediately before the first lip seal provided on the rotor shaft on the high-pressure side of the screw fluid machine. Since the first lip seal is lubricated by the lubricating fluid without applying excessive pressure, the first lip seal life is long.

Embodiments and reference examples of the present invention will now be described with reference to the drawings.
FIG. 1 shows a screw compressor 1 which is a first reference example of the screw fluid machine of the present invention. The screw compressor 1 compresses low-pressure (for example, atmospheric pressure) steam (target gas) (for example, to 0.5 MPaG) with a pair of screw rotors 4 that engage in male and female, housed in the rotor chamber 3 of the housing 2. To be discharged.

  The housing 2 includes a suction flow path 5 for supplying steam to be compressed to the rotor chamber 3, a discharge flow path 6 for discharging steam compressed by the screw rotor 4 in the rotor chamber 3, and a rotor shaft of the screw rotor 4. Bearing shaft sealing spaces 8 and 9 are provided for installing a structure for supporting and sealing the shaft 7 on the suction side and the discharge side, respectively.

  The rotor shaft 7 is rotatably supported by a roller bearing 10 installed in the suction-side bearing shaft sealing space 8 and two ball bearings 11 installed in the discharge-side bearing shaft sealing space 9, The bearing shaft sealing space 9 on the side is extended and connected to a motor (not shown).

  A lip seal 12 is installed on the motor side of the roller bearing 10 to prevent foreign substances (such as grease on the roller bearing 10) from entering the motor side. On the screw rotor 4 side of the roller bearing 10, grease on the roller bearing 10 is installed. Is provided with a lip seal 13 for sealing so as not to flow out to the screw rotor 4 side, and a lip seal 14 for sealing so that steam and lubricating fluid do not enter the roller bearing 10 side from the suction flow path 5.

  A labyrinth seal 15, a first lip seal 16, and a second lip seal 17 are provided in the bearing shaft seal space 9 on the discharge side between the screw rotor 4 and the ball bearing 11 in order from the screw rotor 4 side. The labyrinth seal 15 includes a rotor that is fitted to the rotor shaft 7 and rotates together with the rotor shaft 7, and a known stator that is fitted and fixed to the inner wall of the bearing shaft sealing chamber 9 so as not to contact the rotor. Non-contact seal. The lip seal 16 is installed in a direction to seal the invasion of steam from the labyrinth seal 15 side, and the lip seal 17 is installed in a direction to prevent outflow of grease or the like from the ball bearing 11.

  The bearing shaft seal space 9 is divided by a first lip seal 16 and a second lip seal 17, and a first seal space 18 between the labyrinth seal 15 and the first lip seal 16, the first lip seal 16 and the second lip seal 16. A second seal space 19 between the lip seal 17 and an oil seal space 20 closer to the ball bearing 11 than the second seal space 19 are divided.

  Further, the housing 2 has an open flow path 21 for communicating the bearing shaft sealing space 8 between the lip seal 13 and the lip seal 14 to the outside, and a first seal between the labyrinth seal 15 and the first lip seal 16. A first communication path 22 that opens the space 18 to the atmosphere, a second communication path 23 that opens the second seal space 19 between the first lip seal 17 and the second lip seal 18 to the atmosphere, and a first communication space Further, a lubricating fluid supply passage 24 is provided for supplying the condensed water of the steam discharged from the screw compressor 1 as a lubricating fluid.

  The labyrinth seal 15 causes the steam to leak into the first seal space 18 little by little. The first communication path 22 releases the vapor leaked into the first seal space 18 to the atmosphere, but the first communication path 22 cannot be completely brought to atmospheric pressure due to the flow resistance, and is about 0.02 MPaG. Keep below.

  On the other hand, the hot water in which the high-pressure steam (0.5 MPaG) discharged from the screw compressor 1 is condensed in the demand facility has a pressure of about 0.4 MPaG, for example. Therefore, the condensed water can be supplied into the first seal space 18 without providing a facility such as a pump. Excess condensed water is discharged to the outside through the first communication path 22 together with the steam leaked from the labyrinth seal 15. The steam and condensed water flowing out from the first communication path 22 may be recovered and reused.

  In this screw compressor 1, since the lubricating fluid is supplied to the first seal space 18, even if dry steam leaks from the labyrinth seal 15, the lubricating fluid is not allowed to flow between the first lip seal 16 and the rotor shaft 7. The first lip seal 16 does not contact the rotor shaft 7 in a dry state by interposing the layers, and wear is not promoted. Further, the lubricating fluid takes away the heat generated by the friction between the first lip seal 16 and the rotor shaft 7 and prevents the first lip seal 16 from being deteriorated or damaged by overheating.

  Further, since the second seal space 19 is opened to the atmosphere by the second communication hole 23, even if the seal of the first lip seal 16 becomes defective, the leaked pressure such as vapor is released to the atmosphere. . For this reason, the pressure in the reverse direction is not applied to the second lip seal 17, so that the lubricating oil does not flow out of the sealed oil space 20 or the steam does not enter the sealed oil space 20.

2 and 3 show a bearing shaft seal structure on the high pressure side of a screw expander 31 which is a second reference example of the screw fluid machine of the present invention. In the screw expander 31, a screw rotor 34 is accommodated in a rotor chamber 33 formed in a housing 32, and a rotor shaft 35 of the screw rotor 34 is rotatably supported by a roller bearing 36 and a ball bearing 37 held in the housing 32. doing. In the screw expander 31, a labyrinth seal (non-contact seal) 38, a first lip seal 39 and a second lip seal 40 are disposed between the screw rotor 34 and the bearing 36 in order from the screw rotor 34 side. .

  The labyrinth seal 38 includes three rings 38a, 38b, and 38c formed so that a gap between the rotor shaft 35 and the rotor shaft 35 is several tens of μm or less, and a compression that hermetically presses the rings 38a, 38b, and 38c against the housing 32. Springs 38d, 38e. The steam leaking from the rotor chamber 33 is decompressed by pressure loss every time it passes through a small gap between the rings 38a, 38b, 38c and the rotor shaft 35.

  The first lip seal 39 and the second lip seal 40 are fitted on the rotor shaft 35 and are in sliding contact with a sleeve 41 that rotates together with the rotor shaft 35. The first lip seal 39 is attached in a direction to prevent the leakage of steam and other foreign matters from the rotor chamber 33 side to the roller bearing 36 side, and the second lip seal 40 is lubricated from the roller bearing 36 side. Etc. are attached in a direction to prevent leakage.

  The clearance between the housing 32 and the rotor shaft 35 is between the final stage ring 38c and the first lip seal 39 of the labyrinth seal 38 and includes a compression spring 38e that presses the final stage ring 38c. It is divided into a space 42, a second seal space 43 between the first lip seal 39 and the second lip seal 40, and an oil seal space 44 including the roller bearing 36 and the ball bearing 37. The housing 32 has a lubricating fluid supply passage 45 for supplying lubricating water (lubricating fluid) to the back of the last-stage ring 38c of the first seal space 42, and a first communication for opening the first seal space 42 to the atmosphere. A hole 46 and a second communication hole 47 that opens the second seal space 44 to the atmosphere are formed.

In this reference example , as shown in FIG. 4, the lubricating water supplied to the first seal space 42 is supplied from the boiler 48 to the steam expander 31, and the steam discharged from the steam expander 31 is converted into a heat exchanger 49. A part of the condensed water generated during secondary use is supplied via the steam trap 50. For example, when steam of about 0.8 MPaG is supplied from the boiler 48 to the steam expander 31 and steam of about 0.3 MPaG is discharged from the steam expander 31, the condensed water in the heat exchanger 49 is also about 0.3 MPaG. Has a pressure of Further, in the screw expander 31, the steam leaked through the labyrinth seal 38 is released to the atmosphere through the first communication hole 46, but due to the pressure loss of the first communication hole 45, The pressure is about 0.02 MPaG. That is, since the condensed water in the heat exchanger 49 has a pressure sufficiently higher than the pressure in the first seal space 42, the first seal space can be removed from the lubricating fluid supply flow path 45 without using a pump or the like. 42 can be supplied.

  The temperature of the condensed water of about 0.3 MPaG is about 144 ° C., and this condensed water is supplied to the first seal space 42 to lubricate and friction between the first lip seal 39 and the rotor shaft 35. While reducing, the abnormal temperature rise of the 1st lip seal 39 is prevented. As a result, wear of the first lip seal 39 is prevented, the shaft seal by the first lip seal 39 is maintained, the internal pressure of the second seal space 42 is maintained at atmospheric pressure, and steam and foreign matter to the sealed oil space 43 are maintained. Can be prevented from entering.

FIG. 5 shows a bearing structure on the high pressure side of a screw compressor 51 which is a screw fluid machine of a third reference example of the present invention. In the screw compressor 51, a screw rotor 54 is accommodated in a rotor chamber 53 formed in a housing 52, and a rotor shaft 55 of the screw rotor 54 is rotatably supported by a ball bearing 56 held in the housing 52. In the screw compressor 51, a visco seal (non-contact seal) 57, a first lip seal 58, and a second lip seal 59 are disposed between the screw rotor 54 and the ball bearing 56 in order from the screw rotor 54 side. Yes. The first lip seal 58 and the second lip seal 59 are in sliding contact with the sleeve 60 fitted to the rotor shaft 55.

  The clearance between the housing 32 and the rotor shaft 55 is a first seal space 61 between the Bisco seal 57 and the first lip seal 58, and a second seal between the first lip seal 58 and the second lip seal 59. It is divided into a space 62 and an oil seal space 63 that includes a ball bearing 56. The housing 52 includes a lubricating fluid supply channel 64 that supplies lubricating water to the first seal space 51, a first communication hole 65 that opens the first seal space 51 to the atmosphere, and a second seal space 52 that opens to the atmosphere. The second communication hole 66 is formed.

  The visco seal 57 is formed of a spirally formed protrusion on the rotor shaft 55, and the lubricating water supplied to the first seal space 51 is screwed toward the rotor chamber 53 by the rotation of the rotor shaft 55 to lubricate the rotor shaft 55. The target gas is sealed in the rotor chamber 53 by the fluid pressure of water.

In this reference example , since the lubricating water is supplied to the first seal space 51 via the lubricating fluid supply flow path 64, the visco seal 57 runs out of liquid, and the target gas leaks into the first seal space 51 in a large amount. The first lip seal 58 is in dry contact with the sleeve 60 and overheats, and does not wear out rapidly.

FIG. 6 shows a shaft seal structure on the high-pressure side of a screw compressor 51a which is a screw fluid machine of one embodiment of the present invention. In the present embodiment, the same components as those in the third reference example are denoted by the same reference numerals, and redundant description is omitted. In the screw compressor 51a of the present embodiment, the visco seal 57a includes a sleeve 67 fitted to the rotor shaft 55. A spiral groove is formed on the inner surface of the sleeve 67, and a fluid pressure that moves the lubricating water toward the rotor chamber 53 by the rotation of the rotor shaft 55 is generated.

  In this embodiment, the lubricating fluid supply channel 64 communicates with a through hole 67a formed through a position slightly closer to the ball bearing 56 than the center of the sleeve 67, and supplies lubricating water in the middle of the visco seal 57a. It is like that. In the visco seal 57 a, the generated fluid pressure continuously rises toward the rotor chamber 53. For this reason, if the through hole 67a is located within 2/3 of the total length of the Bisco seal 57a from the ball bearing 56 side, the lubricating water is supplied to the rotor shaft 55 by the pressure of the condensed water of the steam discharged from the screw compressor 51a. And the sleeve 67 can be supplied.

  If lubricating water is supplied in the middle of the Bisco seal 57a as in the present embodiment, the Visco seal 57a does not run out of liquid. Further, since the lubricating water leaked to the first seal space 51 side lubricates and cools the first lip seal 58, the life of the first lip seal 58 can be prevented from being shortened.

The schematic sectional drawing of the screw compressor of the 1st reference example of this invention. Sectional drawing of the bearing structure of the screw expander of the 2nd reference example of this invention. The partial cutaway perspective view of the bearing structure of the screw expander of FIG. FIG. 3 is a schematic view of a system including the screw expander of FIG. 2. The schematic sectional drawing of the bearing structure of the screw compressor of the 3rd reference example of this invention. The schematic sectional drawing of the bearing structure of the screw compressor of embodiment of this invention.

Explanation of symbols

1 ... Screw compressor (screw fluid machine)
DESCRIPTION OF SYMBOLS 2 ... Housing 3 ... Rotor chamber 4 ... Screw rotor 5 ... Suction flow path 6 ... Discharge flow path 7 ... Rotor shaft 9 ... Bearing shaft sealing space 11 ... Ball bearing 15 ... Labyrinth seal (non-contact seal)
DESCRIPTION OF SYMBOLS 16 ... 1st lip seal 16 ... 2nd lip seal 18 ... 1st seal space 19 ... 2nd seal space 20 ... Oil seal space 22 ... 1st communication path 22 ... 2nd communication path 24 ... Shaft seal fluid flow path

Claims (3)

In a screw fluid machine that compresses a target gas by a male and female screw rotor housed in a rotor chamber formed in a housing, or converts an expansion force of the target gas into a rotational force,
Between the high pressure side of the bearing of the rotor shaft of the screw rotor the screw rotor, wherein the screw rotor side in order, the helical grooves causing the lubricating fluid by the rotational force to move the rotor chamber side of the rotor shaft Alternatively, a non-contact seal having a protrusion and a first lip seal are disposed,
A first communication hole that communicates a first seal space between the non-contact seal and the first lip seal with a space equal to or lower than a working pressure of the first lip seal;
A screw fluid machine, comprising: a lubricating fluid supply channel for supplying a lubricating fluid into the spiral groove or projection and supplying the lubricating fluid to the first seal space. A second lip seal is disposed between the first lip seal and the bearing;
2. The screw fluid machine according to claim 1 , further comprising a second communication hole that communicates a second seal space between the first lip seal and the second lip seal to a low-pressure space having a substantially atmospheric pressure. . The target gas is steam, a screw fluid machine according to claim 1 or 2, wherein the lubricating fluid is characterized by a condensed water of the target gas.

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